US2269641A - Machine tool - Google Patents

Description

Jam 1942- R. M. W OYTYCH 2,269,641

MACHINE TOOL Filed June 7, 1 939 6 Sheets-Sheet 3 mg... Qcrg/moxao 777 %y@c/e em'mg E dimqa s v Jan. 13, 1942. 'R. M. 'WOYTYCH 2,269,641

MACHiNE TOOL Filed June 7, 1959 6 Sheets-Sheet 5 Jo'a Jam-13,1942. Ri W YTYC 2,269,641.

MACHINE TOOL Filed June '7, 1939 6 Sheets-Sheet 6 6:1 JJ f (flTTo ays Patented Jan. 13, 1942 T OFFICE MACHINE TOOL Raymond M. Woytych, Fond du Lac, Wis., as-

signor to Giddings & Lewis Machine Tool 00., Fond du Lac, Wis., a corporation of Wisconsin Application June 7, 1939, Serial. No. 277,757

9 Claims.

The invention relates to improvements in machine tools, and has particular reference to a novel attachment which is especially adapted for use with horizontal boring, drilling and milling machines.

A general aim of the present invention is to provide a new and improved machine tool adapted to carry out a continuous-feed facin operation in which a facing tool is moved in a spiral path over a surface being faced.

A more specific object of the invention is the provision of a novel facing attachment adapted to be driven from a tool headstock such, for example, as that of a horizontal boring, milling and drilling machine, and which is arranged to move a facing tool thereon in a spiral path by feeding the tool transversely across the Work piece surface in accurately timed relation with the tool rotation, the attachment being characterized particularly by its compactness, low weight and concentric distribution of. the Weight about its axis of rotation.

Another object is the provision of an attachment of the foregoing character embodying -a novel speed changemechanism of extreme compactness and low weight for adjusting the rate of tool feed transversely of the work piece surface so as to adjust the spacing between convolutions of the spiral to accommodate different degrees of fineness of finish, etc.

Another more general object is to providean improved machine tool affording a wide and flexible range of machining operations including, for example, facing, boring and drilling.

Still another object is to provide an improved attachment adapted to be driven from a tool headstock and by means of which a plurality of tools may be utilized either simultaneously or sequentially to perform a corresponding plurality of machining operations.

Further objects and advantages of the invention will become apparent as the following de-, scription proceeds, taken in connection with the accompanying drawings, in which:

Figure 1 is a front elevational View of a horizontal boring, drilling, and milling machine with an attachment embodying the features 'of the invention.

Fig. 2 is an enlarged front face view of the attachment included in the machine of Fig. 1.

Fig. 3 is a side elevation of the attachment and a fragment of the headstock to which it is attached.

Fig. 4 is a fragmentary view illustrating the use of the attachment with a plurality of facing tools.

Fig. 4a is a diagrammatic face view of the work piece shown in Fig. 4 and illustrating the spiral path of the facing tool.

Fig. 5 is an enlarged front elevational view Fig. 8 is a transverse sectional view along the line 88 in Fig. 5 of the speed-change gearing included in the attachment.

Figs. 9 and 10 are longitudinal, sectional views respectively along the lines 99 and Ill-40 in Fig. 8.

Fig. 11 is a diagrammatic layout of the speedchange gearing.

Fig. 12 is a sectional view along the line l2l2 in Fig. 5.

While the invention is susceptible of various modifications and alternative constructions I have shown in the drawings and will herein describe in detail the preferred embodiment, but it will be understood that I do not thereby intend to limit the invention tothe specific form disclosed, but intend to cover all modifications and alternative constructions falling Within the spirit and scope of the invention asexpressed in the appended claims. r i

For purposes of exemplification, the invention has been shown herein (Fig. 1) as embodied in a horizontal boring, drilling and milling machine. Machines of the type are provided in various forms. In the form selected for purposes of illustration, the machine comprises an elongated horizontal bed Hi above the central portion of which is located a work table, I I. On opposite sides of the table II are an adjustably mounted tailstock column 12 and a headstock column M.

The work table II is slidable endwise along ways 15 fashioned on the top of a saddle I6, which is in turn slidable in a direction transverse to the table along ways I! formed on the top of the bed in. Any suitable means may be provided, available at will for traversing the saddle I6 along the bed In. In the present instance this means comprises a horizontal feed screw l8 which extends along the interior of the bed It) and which at one end is in threaded engagement with a fixed nut I9 on the underside of the saddle Hi. The other end of the screw I8 is operatively connected through a gear transmission mechanism, indicated generally at Zll to an electric drive motor 2| mounted on the right end of the bed 10. A lever 22 is available to control the direction of drive The details of the transmission mechanism per Se constitute no part of the present invention and, hence, are not disclosed herein. A suitable mechanism is shown and described in Patent No. 1,858,491, issued May 17, 1932. to Keith F. Gallimore.

On the tailstock column I2 is a vertically slidable tailstock 23 mounted on ways fashioned on the column. This tailstock is adapted to be traversed along the ways by means of a vertical feed screw 24 operable from any suitable power mean such as the transmission 20.

At the opposite end of the machine, a headstock 25 is slidably mounted on vertical ways 26 v formed on the front face of the headstock column M. The head stock 25 is supported and adapted to be traversed by means of a vertical feed screw 21 connected at its lower end to the power transmission 20. The screws 24 and 21 in the tail stock and headstock columns, respectively, are adapted to be driven in synchronism and to traverse the tailstock 23 and the headstock 25 at the same speeds, the direction of drive being under the control of a hand lever 28. The details of the connections between the transmission 20 and the feed screws I8, 24 and 21, constitute no part of the present invention and, hence, are not disclosed herein. Suitable connections are shown in the above mentioned Gallimore patent.

Rotatable in the headstock 25, and opening through the left end thereof, is a main horizontal spindle member in the form of a sleeve 30. Any suitable means may be provided for driving this sleeve 30, and in the present instance this means is shown as comprising a concentric gear 3| rigid with the sleeve. The gear 3| meshes with a small pinion 32 which is connected through a shaft 33 to a speed-change mechanism 34. The power inlet to the transmission 34 is connected through a train of gears 35, 36 and 31, to a gear 38 slidably splined on a vertically-anchored shaft 39 which extends through the headstock 25, and which is operatively connected at its lower end to the motor 2|.

An elongated tool spindle 4|] extends through and is splined for axial movement in the sleeve 33. Accordingly, the sleeve constitutes a drive member for the spindle 40. The left end of the spindle projects from the headstock 25 and has a transversely slotted outer end to which may be attached a socketed tool holder extension 4| (Fig. 3) in which a boring tool (not shown) may be secured. The spindle 40 may be rotated and fed axially when used to drive such a tool secured to its outer end. Axial adjustment of the spindle 40 may be accomplished either manually or by power and the means for this purpose preferably comprises an elongated parallel gear rack 42 which is anchored at one end by a rotary splined connection 43 to the inner end of the spindle. The free end of the rack 42 meshes with a pinion 44 rotatable with a large worm wheel 45 in a housing 25 on the front of the headstock 25. Meshing with the worm wheel 45 is a worm 46 axially splined on a vertical shaft 41 extending through the housing 25. The lower end of the shaft 41 is adapted to be connected to the transmission 2|] for a power drive. A hand wheel 48 is secured to the upper end of the shaft 41, and affords means for effecting a manual adjustment of the spindle 40. The position of adjustment is indicated by a suitable micrometer 49.

A novel form of facing, boring, drilling and tapping attachment, designated generally by the numeral 50 and herein referred to for the sake of brevity as the facing attachment, is fixed on the forward or left hand end of the sleeve 30 (Fig. 1). This facing attachment or tool support, being fast on the sleeve 30, is rotated with it. In its illustrative form the facing attachment 50 comprises a generally cylindrical or drum shaped housing 5| arranged coaxially with the sleeve 30 and having its rear face bolted to the latter. Extending diametrically across the front face of the housing 5| in a vertical plane are ways 52 (Fig. 2 and see also Fig. '7) on which a tool slid 53 is slidably mounted for endwise movement in a path transverse to and intersecting the axis of rotation of the housing. An elongated central slot 54 is fashioned in the slide 53 to receive the projecting end of the spindle 40 so that the slide 53 may be moved freely along the ways without interfering with the spindle. T slots 55 extending along the face of the slide 53 accommodate the fastening of various boring or facing tools on the slide. For example, in Fig. 3, a facing tool 56 has been shown mounted in a facing tool block 51, which is secured to the slide 53 by bolts 58 having their heads in the T slots. Similarly, a telescopic boring tool designated generally by the numeral 59 has also been shown attached to the slide 53. Various other forms of tools may be secured to the slide such, for example, as an offset boring tool 59 shown in dot-dash lines in Fig. 3.

Briefly stated, facing is, in the present machine, accomplished by moving the facing or scalping tool 56 across a work piece surface in a spiral path so as to cover progressively the area to be faced. For this purpose the tool 56 is fixed to the slide 53 as noted above and the latter is fed along the ways 52 in exact timed relation with the rotation of the housing 5|. To insure proper timing a common power actuator is utilized for imparting both the feeding and rotative motions to the tool. Furthermore, provision is made for adjusting the rate of slide feed with respect to the rate of rotation so as to control the spacing of adjacent convolutions of the spiral, or, in other words, the pitch or tightness of the spiral. The arrangement is preferably such that the slide 53 can be fed at its selected rate either toward or away from the axis of housing rotation so that the spiral path of the tool may be traversed either from its periphery in toward the center or vice versa.

For an example of the type of facing operation contemplated reference may be made to Figs. 4 and 4 In Fig. 4 the facing tool 56 is shown in position for facing or scalping a surface 60 on a work piece 6|, which is of course carried on the table N (Fig. 1). As the housing 5| is rotated and slide 53 traversed in timed relation the tool 56 moves over the work piece surface 63 in a spiral path indicated roughly by the dot-dash line 62 in Fig. 4. At the same time an opposite surface 63 (Fig. 4) on the work piece 6| may be machined by a facing tool 64 fixed on the slide 53 by a gooseneck projecting through a bore 66 in the work piece. Alternatively, a boring tool (not shown) may be fixed on the end of spindle 40, as noted above, and used to machine the bore 66 at the same time the tool 56 is facing the work piece.

To feed the slide 53 in timed relation with the rotation of the attachment housing 5| a drive mechanism (Fig. 6) is utilized embodying a gear 67 carried by a stub shaft 6! journaled in the housing 5|, at a point eccentric to the latters axis of rotation. This gear 61 meshes with a stationary ring gear 68, bolted on the front of the headstock 25, and coaxial with the housing axis. Hence, as the gear 61 rolls about the periphery of the ring gear 68 during rotation of the housing 5| it is rotated in timed relation with the rotation of the attachment housing 5| and, thus in timed relation with the rotation of the facing tool 56. Accordingly, the rotating gear 61 is utilized to feed the slide 53 in its path transverse to the axis of housing rotation. The connection of the gear 61 with the slide 53 includes a change-speed gearing, designated generally by the numeral 69 (Figs. 5 and 7) and to which the gear 51 is connected through a spiral gear I and a pinion II. At the driving end of the speed-change gearing 69 (Fig. a pair of bevel gears 12-13 connect the driven shaft 14 of the gearing with a shaft I5, the other end of this latter shaft being connected through a reversing clutch mechanism I6 with a stub shaft TI. The reversing clutch I6 is controlled automatically, as will hereinafter appear, in conjunction with the speed-change gearing 69 so that rotation of the stub shaft 11 or power take-off device will be unidirectional, irrespective of the setting of the speed-change gearing. The stub shaft TI is in turn connected through a manual- 1y controllable reversing clutch I8 and meshing pinions I9 and 80 with a screw 8|. This screw meshes with an elongated segmental nut 82 fashioned on the edge of the slide 53 (Fig. 7) so that the slide is advanced endwise along the ways 52 by rotation of the screw 8|. The direction of slide feed is, of course, controlled by the reversing clutch I8.

In brief, the slide 53 is fed at a rate depending upon the setting of the speed-change gearing 69, though always in timed relation with the rotation of the attachment housing 5|. Additionally, the direction of slide feed is varied at will by the reversing clutch I8 and stopped completely by shifting this clutch to neutral. The speed-change gearing herein shown is described and claimed as such, in my copending application Serial No. 329,699, filed April 15, 1940, and which application is a division of this present case.

Attention may now be given to a more detailed consideration of the construction of various gearings, etc., included in the slide feed mechanism and heretofore only generally described. Turning first to the speed-change gearing 69, this gearing may be designated as being generally of the drive-key type but it is of a novel form such that gears of small diameter serve to accomplish a wide range of speed adjustments. The use of gears of small diameter is made possible by arranging the gearing so that the various selective gear connections are aditive, each speed setting preferably bearing a true geometric-progression relation to the other settings. In this Way a gearing of small over-all dimensions is achieved, suitable for housing within a compact attachment head. The gearing herein shown is capable of six different speed settings. With respect to the compactness of the attachment it should be noted that the illustrative device is quite thin in an axial direction (Fig. 1) so that there is comparatively little overhang at the end of the spindle sleeve 30. The consequent minimization of overhanging weight on the sleeve is, of course, highly desirable.

In the illustrative construction (Fig. 5) the driving pinion II is fast on a first driving gear cluster including a gear 81 and pinion 84. Coaxial with this gear cluster is a stationary shaft 83 also having loosely journaled thereon two further gear clusters each made up of one of the pinions 85 and 86, and a corresponding one of the gears 88 and 89 (see also Fig. 9). Further, the speed change gearing 69 includes a stationary intermediate shaft 90 (Figs. 8 and and ahollow tubular shaft 9| within which is telescoped the driven shaft I4 (Figs. 5 and 10). On the intermediate shaft 90 are loosely journaled a gear 92 and two gear clusters made up respectively of gears 93 and. 94, as well as pinions 95 and '96. On the shaft 9| six driven gears 9I,-I02

are loosely journaled, which correspond to the,

six different speed settings of the speed-change gearing. To condition the gearing for a selected speed setting, the corresponding one of the driven,

gears is connected to the driven shaft 14 by a drive key I 03 (Figs. 5 and 10). This drive key is of conventional form being yieldably urged,

into engagementwith ,a registering one of the gears by springs I04. Pin I05 holds the drive key inposition on the driven shaft 14 and the nose of the drive key projects through a slot I06 in the side wall of the tubular shaft 9| into engagement with a slot in the hub of the registering one of the driven gears (Fig. 8).

To shift the drive key I03 axially of the tubular shaft 9| into engagement with a selected one of the driven gears 9'I-|02, a manually operable speed selection mechanism is provided. ,This. mechanism includes a stub shaft I01 (Fig. 2) projecting from the attachment housing 5| and having a squared end to receive a hand crank I (not shown). A dial I08 indicates the speed setting. Fast on the stub shaft I0! is a pinion I09 (Fig. 5) meshing with a circular toothed rack IIO on the free end of the shaft I4 so that rotation of the pinion I09 serves to shift the shaft 14 axially and to bring the drive key I03 into engagement with the desired one of the driven gears.

The various trains of gears which are active for the different speed settings can best be seen by reference to the diagrammatic layout in Fig. 11. In this layout or development of the gearing th series of driven gears have been reproduced at both the top and bottom of the figure. I

Driven gear g g gg Gear train to selected driven gear driven shaft From an inspection of the foregoing tabulation it will be seen that the various driven gears are 92 and the gears in the various clusters. Though the pinions are of the same diametrical pitch as the gears they may have any particular desired ratio of tooth number to that of the corresponding gears depending upon the speed reduction desired. By way of example, the pinions may all have eighteen teeth and the gears all thirty-three teeth. In such case the ratios of speeds for the six different settings of the gearing constitute a geometric progression, which is an especially desirable relation since from such a. series may b quickly and easily selected a suitable pitch for the facing tool spiral requisite for a particular facing operation.

Th speed-change gearing 69 described above is such that the direction of rotation of the driven shaft 14 is reversed for alternate settings of the speed-change gearing. It is desirable, however, that the shaft 11 (Fig. be driven unidirectionally despite changes in speed as previously noted and, accordingly, the reversing clutch 16 is arranged to be automatically actuated in accordance with the setting of the speedchange gearing so as to compensate for the reversals in the speed-change gearing. For this purpose a three lobe peripheral cam III (Figs. 5 and 12) is fixed on the setting-control shaft I01 of the speed-change gearing. An axially slidable cam follower rod I I2 is urged against the cam III by a compression spring H3 bearing against a collar H3 pressed against a shoulder on the rod (Fig. 12). A clutch shifter shoe H4 slidably carried on the rod H2 serves to shift a toothed clutch driver H5, which is splined on the shaft 15, into engagement with one or the other of the toothed driven clutch members II6-I I1. The cam III is indexed a sixth of a revolution for each step in the gear setting so it alternately brings a lobe and a depression into engagement with the cam follower rod H2 with the result that the upper and lower clutch members I IG-I I1 are alternately engaged.

To avoid jamming and breakage of the clutch by positive actuation of it by the cam III when the clutch teeth are not in registry, a. yieldable connection is used between the cam follower rod H2 and shifter shoe H4. For this purpose a second compression spring H8 is interposed between the shifter shoe and a collar H8 pinned on the rod. With this arrangement when the rod I I2 is pushed downward (as viewed in Fig. 12) by the cam III, the thrust transmitted from th rod I I2 through collar H8 and spring H8 compresses the lower spring I I3, thereby permitting the shifter shoe H4 to move down and engage the clutch driver H5 with the lower clutch member H1. In the event that the teeth on clutch parts I I5 and I I1 are not in registry at the instant the rod H2 descends, however, the spring H8 is also compressed to store up the thrust force and thereafter expands to push the shifter shoe H4 down as soon as the teeth do register on further rotation of the shaft 15. Similarly, when the upper end of the rod H2 rides into a low point on the cam III the spring H3 is released to thrust the rod H2 and shifter shoe H4 upward. Since this upward thrust is applied by a yieldable spring, however, final upward movement of the clutch driver H5 to engage the driven member H6 does not take place until the mating teeth are in registry.

Bevel gears II 9-I2Il on the clutch driven members I I6-I I1 respectively mesh with a bevel gear I2I (Fig. 5) on the shaft 11, so that this shaft is driven through one or the other of the clutch gears II 9--I 20 depending upon the setting of the reversing clutch. Since the cam III is shifted coincidentally with changes in the speed-change gear setting the reversing clutch automatically retains the rotation of the shaft 11 unidirectional.

In order to control the direction of feed of the tool slide 53 the manually operable reversing clutch 18 is interposedbetween the unidirectional shaft 11 and the screw 8I which meshes with the segmental nut on the slide (Fig. 5). This reversing clutch I8 is of conventional form and embodies a shiftable clutch driver I22 spllned on the shaft 11. This driver is shiftable from its neutral position illustrated alternatively into engagement with one or the other of the clutch driven members I23 or I24. A hand lever I25 on the front face of the attachment casing (Figs. 2 and 7) serves, upon oscillation, to shift the clutch driver I22 into either neutral, forward or reverse positions. When the clutch driver I22 is engaged with the driven member I23 the drive is completed directly from the shaft 11 through a pinion I21 fast on the clutch driven member I23 and through pinions 19 and to the screw 8|. Similarly, when the clutch shoe I22 is engaged with the other clutch driven member I24 a drive in the opposite direction is completed from the shaft 11 through a bevel gear I28 fast on the driven member I24, thence through an idler bevel gear I29 to the bevel gear I30, which in turn remains connected at all times with the screw 8| through pinions I9 and 80.

In addition to the power feed described above for the slide 53 provision is also made for manual adjustment of its position. Manual actuation is particularly desirable for accurate positioning of the slide to determine the diameter of a bore to be machined by a boring tool carried on the slide. To provide for such manual adjustment of the slide the outer end of a stub shaft I26 (Fig. 5) which carries the bevel gear I29 is socketed to receive a suitable hand wrench (not shown). By turning this shaft I26 the slide driving screw 8I is rotated through gears I29, I30 and pinions I21, 19 and 80. A micrometer dial I 26 on the side of the attachment head (Fig. 3) indicates the position of slide adjustment.

Brief re'sum of operation Assuming that it is desired to use only the facing tool 56 (Fig. 3) for making a spiral facing cut, the machine is first adjusted for the desired rate of feed for the tool holder slide 53. For this purpose the speed-change gearing 69 is set for the desired slide feed speed by turning the setting-control shaft I01 (Fig. 2). While the clutch controller I25 is in its neutral position the slide 53 is adjusted by hand, by turning shaft I26 (Fig. 3) as previously described, to bring the facing tool to the desired starting position. Then the clutch control lever I25 (Fig. 2) is shifted to connect the main clutch 18 (Fig. 5) for the desired direction of slide feed. After these preliminary operations rotation of the headstock sleeve 30 is started whereupon the facing tool is automatically traversed through a spiral path across the work piece face by the combined rotative and traversing movement imparted to it. The traversing of the slide 53 is accomplished in timed relation with the attachment rotation since the slide is driven from the gear 61 (Fig. 6) rolling about the fixed ring gear 68, through the medium of the speed-change gearing 69 (Fig. 5)

socketed extension 4| on the spindle 40 (Fig. 3).

The spindle 40 is advanced by either power or hand feed as previously described. Since this spindle projects through the center slot 54 in the slide 53 (Fig. 2) it does not interfere in any way with the latters traversing motion.

The slide 53 may also be utilized for carrying a boring tool, such as the tool 59 (Fig. 3), rather than :a facing tool. In such case the slide is adjusted along its ways by the hand adjustment shaft I26 until the tool is accurately located for the desired diameter of bore. The clutch I8 is, of course, left in neutral during the boring. To accomplish relative feeding motion of the tool and work axially of the bore, the saddle l6 (Fig. 1) is traversed along the ways I1.

I claim as my invention:

1. For use in a machine tool having a rotatable drive member, a tool support attachment embodying a housing rotatable with said drive member, said housing being formed with a guideway transverse to the axis of rotation, a tool holder slide mounted on said guideway, and means including a speed-change gearing mounted within said housing for traversing said slide along said guideway in timed relation to the housing rotation and at a speed determined by the setting of said speed-change gearing, said speed-change gearing including a plurality of gears arranged to be driven in a series gear train, a plurality of independently rotatable driven gears each meshing with a different gear in said train, and means for connecting any selected one of said driven gears in driving relation with said slide.

2. For use in a machine tool having a rotatable drive member, a tool support attachment embodying a housing rotatable with said drive mem-- ber, said housing being formed with a guideway transverse to the axis of rotation, a tool holder slide mounted on said guideway, means including a speed-change gearing mounted within said housing for traversing said slide along said guideway in timed relation to the housing rotation and at a speed determined by the setting of said speed-change gearing, said speed-change gearing including two sets of gear clusters arranged with the clusters in each set coaxial and the axes of the two series parallel, each of said clusters embodying a pinion and a gear coaxially arranged and fixed together, said clusters in both of said sets being arranged in a single series train with the pinion of each cluster in one set meshing with the gears in the other set of clusters, a plurality of independently rotatable drivengears each meshing with a different one of the cluster gears. and means for connecting any selected one of said driven gears in driving relation with said slide.

3. In a facing attachment of the type set forth, the combination of a rotatable housing, a tool holder slide mounted for traversing movement on said housing along a path transverse to the axis of housing rotation, power actuated means within said housing for traversing said slide in timed relation with the housing rotation, said last mentioned means including a reversing mechanism comprising a pair of bevel gears each meshing with a third bevel gear, a driving member and a clutch shiftable from a central position alternatively to connect one or the other of said bevel gears to said driving member, driven means operatively connecting said slide in driven relation at all times to one of said pair of bevel gears so that the slide is driven from said driving member through said one bevel gear alone or through all three of said bevel gears in series in the corresponding alternative engaged posi tions of the clutch and is disconnected from the driving member when the clutch is in neutral, and manualy operable means for rotating said third bevel gear to traverse said slide by hand.

4. In a facing attachment of the type set forth, the combination of a rotatable housing, a tool holder slide mounted for traversing movement on said housing along a path transverse to the axis of housing rotation, power actuated means within said housing for traversing said slide in timed relation with the housing rotation, said last mentioned means including a reversing mechanism comprising a pair of bevel gears each meshing with a third bevel gear, a driving member and a clutch shiftable from a central position alternatively to connect one or the other of said bevel gears to said driving member, driven means operatively connecting said slide in driven relation at all times to one of said pairs of bevel gears so that the slide is driven from said driving member through said one bevel gear alone or through all three of said bevel gears in series in the corresponding alternative engaged ,positions of the clutch and is disconnected from the driving member when the clutch is in neutral, manually operable means for rotating said third bevel gear to traverse said slide by hand, and dial means coacting with said third bevel gear to indicate continuously the position of said slide whether it is moved by power or by hand.

5. In a machine tool, the combination of a rotatable tool spindle, a facing attachment including a generally cylindrical hollow casing with a closed front face, said casing being fixed to said spindle coaxial therewith for rotation with the same, a guideway on the front face of said casing extending generally diametrically across the same, a tool-supporting slide movable along the same, a stationary gear concentric with the axis of housing rotation, a drive gear mounted on said housing in mesh with said stationary gear to roll around the same in the course of housing rotation, a speed-change mechanism including a plurality of rotatable gears connected in driven relation to said drive gear and disposed within said casing at one side of its center with their axes of rotation forming chords with the cylindrical casing, a fixed nut on the slide, a rotatable screw driven by said speed-change mechanism and meshing with said nut, and said screw being journaled within the housing on the side thereof diametrically opposite said speedchange mechanism and with its axis of rotation paralleling those of the gears of said mechanism.

6. A facing attachment of the type set forth, comprising, in combination, a rotatable cylindrical hollow casing having a guideway extending generally diametrically across one end of said casing, a tool-supporting slide traversable along the guideway, power actuated means within the casing for traversing said slide including a speed change gearing and a first rotatable toothed member meshing with a second complemental toothed member fixed to the slide, and characterized particularly by the disposition of said speed-change gearing and said pair of toothed members within said casing and on diametrical- 1y opposite sides of the axis of rotation thereof to minimize the over-all diameter of the casing.

7. A facing attachment of the type set forth, comprising, in combination, a rotatable cylindrical hollow casing having a guideway extending generally diametrically across one end thereof, a tool-supporting slide traversable along the guideway, power actuated means within the casing for traversing said slide including a speedchange mechanism, a reversing mechanism and a first rotatable toothed member meshing with a second toothed member fixed to the slide, and characterized particularly by the disposition of said power actuated means within said casing with said speed-change mechanism on one side of the casing axis of rotation and said reversing mechanism, as well as said pair of toothed members on the diametrically opposite side of said axis to minimize the over-all diameter of the casing and to distribute the weight of the parts within said casing concentrically about its axis of rotation.

8. In a facing attachment of the type set forth, the combination of a drive apparatus including a speed-change mechanism and a reversing mechanism disposed in spaced relation with rotatable elements of each mechanism having their axes of rotation parallel, means including a shaft transverse to said axes and extending between said mechanisms adjacent corresponding ends thereof for interconnecting the same in the form of a generally U-shaped assembly, a rotatable cylindrical casing arranged to house said mechanisms with said U-shaped assembly disposed therein to embrace the axis of rotation of the casing, a tool-carrier slide, guide means supporting said slide for movement on one end of said casing generally diametrically across the same, and means for connecting said slide in driven relation with said drive apparatus.

9. For use in a machine tool having a rotatable drive member, a unitary tool support attachment embodying a housing, means for detachably supporting said housing on the machine tool for rotation adjacent said drive member, said housing having a guideway thereon sustantially transverse to the axis of housing rotation, a tool holder slide traversable along said guideway, {power actuated means encompassed within said housing for traversing said slide along said guideway in a direction independent of the direction of housing rotation and at a feed speed bearing a selectively variable ratio to the angular speed of housing rotation, said power actuated means including a driver element adapted to be revolved in timed relation with the rotation of said housing as well as a reversing mechanism and a speed-change gearing interposed between said driver element and said tool holder slide and all encased within said housing so as to be applicable as a unit to the machine tool.

RAYMOND M. WOY'I'YCH.

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